Valve for Switching Fluids, Extinguishing System, and a Method

ABSTRACT

A sectional valve includes a working valve and a control valve, which controls the working valve. In order to permit a greater flexibility with respect to possible settings and/or use or operation by comparison to known solutions, it is proposed, for example, that the control valve have a control spring ( 34, 34 ′), which presses the anchor ( 5 ) onto the control valve seat ( 17 ), and against which the control coil ( 26 ) lifts the anchor ( 5 ) from the control valve seat ( 17 ), a permanent magnet ( 29 ), which in an actuation state is configured to hold the anchor ( 5 ) lifted from the control valve seat ( 17 ) by the core ( 35 ), and a magnet holder ( 28 ), in and/or on which the permanent magnet ( 29 ) is held in the actuation state, and which permits a distance from the permanent magnet ( 29 ), and/or that the control valve is configured to variably position the core ( 35 ) along a force generated by the control spring ( 34, 34 ′).

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a National Stage of International Application No.PCT/EP2016/051659, filed Jan. 27, 2016 (now WO 2016/134909A1), whichclaims priority to German Application No. 10 2015 203 486.0, filed Feb.26, 2015. The entire disclosures of each of the above applications areincorporated herein by reference.

FIELD

The present disclosure relates to a valve for switching fluids, inparticular a sectional valve for an extinguishing agent line, anextinguishing system with such a valve, and a method for controlling avalve for switching fluids, in particular a sectional valve for anextinguishing agent line.

BACKGROUND AND SUMMARY

For example, solenoid valves, which use a permanent magnet, with which apiston or anchor of the valve is held in a predetermined position, areknown from DE 103 24 091 A1, EP 0 340 625 B1, EP 0 710 790 B1 and WO94/23435 A1.

The solenoid valves described in these documents all share in commonthat their structure only allows a slight flexibility in terms ofpossible settings, and virtually no flexibility with respect to theiruse or operation.

During the application of solenoid valves from DE 103 24 091 A1, EP 0340 625 B1, EP 0 710 790 B1 and WO 94/23435 A1, for example, there is noway to manually open or manually close the valve, since an electricalpulse on a coil provided for this purpose must be generated forrespectively moving the piston or anchor into a position in which thevalve is closed, and/or a position in which the valve is open. Given avalve that in this way requires power or energy to be opened, operationis thus not possible in the event of a power or energy outage. Theramifications of a power or energy outage are especially critical inparticular in the field of extinguishing technology.

In addition, the structural design determines the force to be applied bythe coils to move the piston or anchor, and thus the minimum electricalcurrent to be conducted by the coils. This is disadvantageous, in thatlimitations are placed on the possible actuation, making it harder toreplace a valve with another valve having another current requirement.It is possible to provide a separate actuation for a respective valvethat provides the necessary minimum current. However, this constitutesan additional outlay, which affects the costs of the valve on the onehand, and poses an additional vulnerability to failure on the other.Various models could be provided already while configuring the basicvalve, which are geared toward the respective standard. However, this isassociated with a diversification of the manufacturing process, whichalso leads to increased costs, especially since limits are still placedon application even given a range of standards.

In light of the above, the object of the present disclosure is toprovide a valve for switching fluids, in particular a sectional valvefor an extinguishing agent line, which by comparison to the knownsolutions has a greater flexibility with respect to possible settingsand/or use or operation. The disclosure is also geared toward acorresponding extinguishing system and a method for controlling such avalve, in particular such a sectional valve, for an extinguishing agentline.

A sectional valve is here understood as a valve in an extinguishingagent line with which a portion of the extinguishing agent line in whichpressurized extinguishing agent is present is separated from anunpressurized portion of the extinguishing agent line (that can alsotransition directly into an end of the extinguishing agent line).Extinguishing agents can be present in the unpressurized portion of theextinguishing agent line, wherein this portion can also be empty (e.g.,filled with air).

A first aspect of the disclosure proposes a valve for switching fluids,in particular a sectional valve for an extinguishing agent line, with acontrol valve and a working valve, which is designed for pilot controlby the control valve, with a throttle bore that establishes a firstfluid connection between an inlet of the valve to be pressurized and apiston chamber of the working valve, and a working piston with a firstend face opposite the piston chamber that is larger than a second endface opposite the inlet, wherein the control valve is configured to openand close a second fluid connection between the piston chamber and anoutlet of the valve, wherein the control valve further has: a controlvalve seat, an anchor that closes the second fluid connection togetherwith the control valve seat when pressed onto the control valve seat, amagnetizable core and a control coil configured to exert a magneticforce on the anchor, such that the control coil lifts the anchor fromthe control valve seat to an extent that the second fluid connectionallows a greater flow than the first fluid connection, wherein thecontrol valve has a) a control spring, which presses the anchor onto thecontrol valve seat, and against which the control coil lifts the anchorfrom the control valve seat, a permanent magnet, which in an actuationstate is configured to hold the anchor lifted from the control valveseat by means of the core, and a magnet holder, in and/or on which thepermanent magnet is held in the actuation state, and which permits adistance from the permanent magnet, and/or b) a permanent magnet, whichpresses the anchor onto the control valve seat by means of the core, andagainst the retaining effect of which the control coil lifts the anchorfrom the control valve seat, a control spring, which in an actuationstate is configured to hold the anchor lifted off of the control valveseat, and a magnet holder, in and/or on which the permanent magnet isheld, and which allows a distance from the permanent magnet for atransition into the actuation state, and/or wherein the control valve isconfigured to variably position the core along a force generated by thecontrol spring.

A further aspect of the disclosure proposes an extinguishing system withan extinguishing agent line and a valve according to the disclosure.

Another aspect of the disclosure proposes a method for controlling avalve for switching fluids, in particular a sectional valve for anextinguishing agent line, wherein the valve has a control valve and aworking valve, which is configured for pilot control by the controlvalve, with a throttle bore that establishes a first fluid connectionbetween an inlet of the valve to be pressurized and a piston chamber ofthe working valve, and a working piston with a first end face oppositethe piston chamber that is larger than a second end face opposite theinlet, wherein the control valve further has: a control valve seat, ananchor that closes the second fluid connection between the pistonchamber and an outlet of the valve together with the control valve seatwhen pressed onto the control valve seat, a magnetizable core and acontrol coil configured to exert a magnetic force on the anchor, whereinthe control valve is used to open and close the second fluid connection,wherein the anchor is lifted from the control valve seat during theopening process to an extent that the second fluid connection allows agreater flow than the first fluid connection, wherein a) in an actuationstate, the anchor lifted from the control valve seat against a controlspring that presses the anchor onto the control valve seat is held bymeans of the core via a permanent magnet, wherein the permanent magnetin the actuation state is held in and/or on a magnet holder, wherein thepermanent magnet is removed to end the actuation state, and/or b) beforean actuation state, the anchor is pressed onto the control valve seat bymeans of the core via a permanent magnet, wherein the control coil isconfigured to lift the anchor from the control valve seat against aretaining effect of the permanent magnet, wherein the permanent magnetis held in and/or on a magnet holder, and the permanent magnet isremoved for transitioning into the actuation state, wherein in theactuation state, the anchor lifted from the control valve seat is heldby a control spring, and/or with a step of setting a force to be appliedby the control coil to achieve the actuation state by variablypositioning the core along a force generated by the control spring.

In the present conjunction, “pressing the anchor onto the control valveseat” is understood as brining the anchor and control valve seat intocontact, such that the anchor and control valve seat together close thesecond fluid connection. The term “pressing” here relates to producing asealing pressing force between the anchor and control valve seat, andmust here not be construed as being limited only to arranging the anchorbetween the pressing element and the control valve seat, and as theforce acting on the anchor being directed toward the control valve seat,since the compression force, and hence the desired seal, can also beachieved by pulling the anchor into the control valve seat, i.e., givena suitable arrangement where a force acts on the anchor that is directedaway from the control valve seat (see FIG. 2 of EP 0 710 790 B1).

On the one hand, the disclosure is based on the knowledge that theability to remove the permanent magnet from the valve (or its functionallocation on the valve) is associated with manually switching the valve.If the permanent magnet serves to hold the anchor in the actuation state(i.e., in a state in which the sectional valve was actuated and isopen), this actuation state can be canceled by removing the permanentmagnet, so that the valve closes. By contrast, if the permanent magnetkeeps the valve closed, removing the permanent magnet can yield atriggering in an actuation state. Given a suitable structural design ofthe sectional valve, it is also possible to combine these variants witheach other.

On the other hand, it was recognized that a variable positionability ofthe core relative to its penetration depth brings with it a variablelift of the anchor, which can be used to adjust the desired or requiredattraction force of the control coil, since the acting magnetic force ofthe coil depends on the relative position of the control coil andanchor.

The control spring here acts indirectly or directly between the core andanchor, wherein the function of the control valve in terms of openingand closing the second fluid connection is only associated with amovement of the anchor, wherein the core remains at least essentially inits (variably adjustable) position.

The valve according to the disclosure is preferably provided as asectional valve for an extinguishing agent line, so that the sectionalvalve is preferably configured for a pressure of the extinguishing agentin the inlet ranging from 5 to 400 bar, particularly preferably rangingfrom 10 to 140 bar.

Removing the permanent magnet must not be understood to mean that thepermanent magnet would thus necessarily have to be completely separatedfrom the remaining valve. For removal purposes, it is enough that thepermanent magnet be removed from its normal position, in which it actson the core (and hence possibly indirectly on the anchor), to a pointwhere the effect of the permanent magnet is practically eliminated or atleast reduced to under a threshold that equates to an elimination. Forexample, if the permanent magnet holds the anchor via the core againstthe force of the control spring, removing the permanent magnet is to beunderstood as moving the permanent magnet away from the core until theforce of the control springs exceeds the retaining force exerted by themagnet on the anchor. Even if the permanent magnet is completely removedfrom the magnet holder, the permanent magnet can still be coupled withthe valve as such, for example by means of a loss prevention device.

In an embodiment of the disclosure, the control valve is configured togenerate a releasing magnetic field, which counteracts a retainingeffect of the permanent magnet, wherein the control coil and/or areleasing coil are provided for generating the releasing magnetic field.

The releasing magnetic field can have a force effect that acts on theanchor in a region spatially separate from the permanent magnet on theone hand, and also act to weaken the magnetic field of the permanentmagnet on the other (i.e., overlap the magnetic field of the permanentmagnet and possibly even extinguish it). In this way, the releasingmagnetic field can be used to control the valve. It is here possible toalso use the control coil for generating the releasing magnetic field,even given a reversed direction of flow.

In a configuration of the above embodiment, the releasing coil isprovided in the magnet holder.

Given a releasing coil provided in the magnet holder, actuating (i.e.,applying a current to) the releasing coil makes it possible to influencethe effect of the permanent magnet, so that its effect is selectivelyeliminated or at least diminished to the extent necessary.

In another embodiment in which the valve has the permanent magnet andmagnet holder, the magnet holder is removable.

It is not necessarily the case that the permanent magnet is removed outof or from the magnet holder or shifted inside of the magnet holder forremoval purposes, since the magnet holder itself or at least a portionthereof can be removable in design. It is also possible both that themagnet holder can be removable, and that the magnet can be removed outof or from the magnet holder.

In another embodiment in which the variable positionability of the coreis present, the core is screwed, latched, clamped, bonded and/orpositioned with spacers into a guide bushing of the control valve.

The guide bushing of the control valve ensures a desired positioning ofthe core along a (longitudinal) axis defined by the force generated bythe control spring, wherein the core can be positioned at variouslocations (continuously or incrementally) along this axis, for exampleto bring the lift of the anchor to a desired level in this way.

It can here be provided that, once a desired position has been set, thecore is fixed in this position, for example by welding, bonding,soldering, wedging, countering or in some other suitable way.

In one configuration of the present embodiment, the anchor can be liftedoff of the control valve seat by partially unscrewing or loosening thecore from the guide bush.

If the variable positionability of the core is retained in the use stateof the valve, the position of the anchor can also be influenced, in thatthe anchor is entrained by the core when being unscrewed or otherwisemoved out of the guide bush, and thereby lifted off of the control valveseat. This provides another way of manually operating the valve.

In another configuration, the control valve is designed to screw and/orlatch the core into the guide bushing with the permanent magnet held inand/or on the magnet holder, and subsequently lift the anchor held bythe permanent magnet via the core from the control valve seat.

The combination of permanent magnet and core must be brought closeenough to the anchor for the magnetic force to outweigh the force of thecontrol spring. Given a variable positionability of the core, the core(together with the permanent magnet) can initially be brought closer tothe anchor, so that the anchor adheres to the magnetized core, so thatthe anchor can then be taken along given a counter-movement of the core.

Also described here is a valve for switching fluids, in particularhaving the features in the present disclosure as defined in claim 1,with a working valve seat, into which the working piston can be pressedto separate the inlet and outlet, in particular by means of a workingspring, wherein the working valve seat can be moved along the workingdirection of the piston (e.g., along a force generated by the workingspring), wherein the working valve seat is configured to be exposed to avalve seat force and follow the movement of the working piston with theworking piston pressed into the working valve seat, at least with theinlet pressurized and the working valve closed.

The valve described here preferably has features that are indicated andexplained further above and with reference to the exemplary embodimentsregarding the control valve. However, the features of the working valveenumerated here can be regarded as an independent disclosure takenseparately, so that the valve described here could also be configuredwith a control valve or the like that does not have the featuresenumerated in claim 1.

Described here in particular is a valve for switching fluids, inparticular a sectional valve for an extinguishing agent line, with: aninlet to be pressurized and an outlet, a working piston that can bemoved along a working direction, and a working valve seat, wherein theworking piston and working valve seat are together configured to openand close at least one direct fluid connection between the inlet andoutlet, wherein the valve is configured at least to close the fluidconnection for exposing the working piston to a working piston force,wherein the working valve seat can be moved along the working direction,and the valve is configured at least to close the fluid connection forexposing the working valve seat to a valve seat force, wherein theworking valve seat is configured to follow a movement of the workingpiston with the working piston pressed into the working valve seat, withthe fluid connection closed and the inlet pressurized.

During the operation of an extinguishing system, for example, pressuresurges can arise in the extinguishing agent, i.e., brief pressure spikesor rises. In a conventional valve with piston and valve seat, it maycome about that the piston is briefly lifted from the valve seat duringsuch a pressure spike, so that the valve at least briefly becomespermeable.

It has been recognized that such a behavior with a movable working valveseat can be suppressed or even eliminated, since the working valve seatfollows the piston moved by the pressure surge, thereby at leastreducing the undesired permeability of the valve.

In a configuration of the valve described above, the valve seat forcecan be produced by a working valve spring and/or a difference in areabetween an end face of the working valve seat relative to the workingpiston, and an end face of the working valve seat relative to the inlet.

In particular using an area difference to produce or support the valveseat force is advantageous, since a proportionality or at least aproportional percentage of valve seat force to the height of thepressure spike is here obtained, so that the valve seat force alsoincreases given a higher pressure spike, allowing the working valve seatto follow the piston more quickly. The working valve spring can beadvantageous if the applied pressure is (still) very low, so as toensure a minimum force. Let it be noted that the “and/or” linkage in thepreceding paragraph must be understood to mean that emphasis is therebyplaced on three variants, specifically, first, that the valve seat forceis produced by a combination of the effects of the working valve springand area difference, second, that the valve seat force is produced bythe effects of the working valve spring (without or even against theinfluence of an area difference), and third, that the valve seat forceis produced by the effect of the area difference (or the differentialpressure resulting therefrom) (without or possibly against a springeffect). However, it is here also not precluded that a suitableconfiguration of the valve can also be switched between these variantswithout any fundamental conversion of the valve (i.e., in particularduring operation), even if an embodiment without this type of switchingwould be advantageous given the simpler structural design.

In a valve described here with a movable working valve seat, themovability of the working valve seat can be limited by the liftingrange, in which the valve remains closed, wherein the lifting range canbe comprised in particular of a respective stop above and below the endfaces of the working valve seat.

In the movable working valve cylinder, a seal is advantageously arrangedbetween the upper end face of the working valve seat and the end face ofthe working piston directed toward the inlet.

Further described here is a valve for switching fluids, in particularhaving the features in the present disclosure as defined in claim 1,and/or having the features listed here with respect to the working valveseat that can move along the force produced by the working spring,wherein the valve has a fluid flow signal generator with a bushing and asignal piston guided in the bushing with an outlet end face, to which apressure prevailing in the outlet of the valve is applied, wherein thesignal piston is held in a resting position by a signal spring in anunpressurized state, and a) the signal piston extends outwardly throughthe bushing, so that a position of the signal piston is discernible fromoutside, and/or b) the valve has a detection means for detecting apredetermined deviation of the signal piston from the resting position.

The valve described here preferably has features that were indicated andexplained further above, both in general and with reference to theexemplary embodiments relating to the control valve, as well as thosedescribed here in relation to the movable working valve seat. However,the features of the fluid flow signal generator enumerated here can beregarded as an independent disclosure taken separately, so that thefluid flow signal generator described here could also be used in a valvefor switching fluids, in particular a sectional valve, or the like,which does not have the features enumerated in claim 1.

Described here in particular is a valve for switching fluids, inparticular a sectional valve for an extinguishing agent line, with aninlet and an outlet, wherein a fluid conducting connection between theinlet and outlet is closed with the valve in a resting state, whereinthe valve has a fluid flow signal generator with a bushing and a signalpiston guided in the bushing with an outlet end face, to which thepressure prevailing in the outlet of the valve is applied, wherein thesignal piston is held in a resting position by a signal spring in anunpressurized state, and a) the signal piston extends outwardly throughthe bushing, so that a position of the signal piston is discernible fromoutside, and/or b) the valve has a detection means for detecting apredetermined deviation of the signal piston from the resting position.

Conventional valves for switching fluids, such as sectional valves, donot provide for any integrated state representation, so that taking alook just at the inlet, valve and outlet area does not make it clearright away whether an actuation state (i.e., an open valve) is present.One way of arriving at a state representation is to display the signalused for actuation or show that the control signal was received.However, this does not yet ensure that this state representation alsoreflects the actual state, since even given a received actuation signal,a mechanical malfunction in the valve itself can prevent the workingvalve from actually being open.

The signal piston is exposed to the pressure inside of the valve outlet,and can used to easily realize such a state representation.

Let it be noted that the aforementioned bushing need not necessarily bea component separate from the valve body or the like. While the term“bushing” does also encompass this type of separate component built intothe valve body or the like, it is also already realized by an opening(e.g., bore) in the valve body or housing of the valve. In other words,in the case of such an opening or bore, the housing of the valve or thevalve body itself can be regarded as the bushing.

In a configuration of the described valve, the predetermined deviationis detected by a closing and/or opening of a mechanical, electrical,magnetic and/or optical contact given at least the predetermineddeviation of the signal piston from the resting position.

Possible detection means include any elements or units with which thepredetermined deviation can be detected, such as in particularmechanical or electromechanical switches, electrical contacts (contactbetween which is closed or opened by the deviation), reed contacts, Hallprobes or light barriers.

In another configuration of the above valve, the signal piston has aseal relative to the bushing, which is located between the outlet andsignal spring and/or in an outer wall of the bushing.

If the outlet is sealed relative to the signal spring, the signal springis not exposed to the extinguishing means (or another fluid that flowsthrough the valve and/or is present in the outlet), with a (nalternative or additional) seal also being possible between the signalpiston and the bushing in the outer wall of the bushing.

In another configuration of the above valve, the signal piston, inparticular given an unpressurized outlet, can be moved through exposureto an outside force in the direction of the outlet and/or opposite thisdirection to check the function.

A corresponding actuation from outside, for example by a user wishing tocheck the functionality of the signal piston and then indirectly of thevalve as well, makes it possible to pull out the signal piston and/orpress it into the valve, so that any blockage or other operationalimpairment can be recognized.

In another configuration of the valve, signal pistons and signal springsare dimensioned in such a way that the signal piston comes to abutagainst the bushing given a predetermined pressure in the outlet.

On the one hand, the abutment of the signal piston against the bushingcan be used as an indication that the predetermined pressure was reachedor is present, wherein a corresponding marking or designation can enablean easier recognition of the abutment. Just as any intermediateposition, the abutment itself can in turn be detected by the detectionmeans as an example of a predetermined deviation of the signal pistonfrom a resting position.

On the other hand, if a corresponding seal or the like is provided inthe area of the abutment, the abutment can also be used to achieve anadditional sealing effect that is required or would be desirable abovethe predetermined pressure.

DRAWINGS

The disclosure will be described in greater detail below based onpreferred exemplary embodiments, with reference to the attacheddrawings. Shown on:

FIG. 1 is a first exemplary embodiment of a sectional valve according tothe disclosure in a resting state;

FIG. 2 is a second exemplary embodiment of a sectional valve accordingto the disclosure comparable to the one on FIG. 1 in the actuationstate; and

FIG. 3 is an exemplary embodiment of a method according to thedisclosure for controlling a valve for switching fluids based on theexample of a sectional valve.

DETAILED DESCRIPTION

A sectional valve according to the disclosure is described in thefollowing discussion of the exemplary embodiments of the disclosure. Letit here be noted that the discussions of the flexible valve seat of theworking valve and the signaling device are also to be understood asbeing independent of the details involving the control valve of thesectional valve, even if these explanations are described as preferredand advantageous exemplary embodiments of the disclosure.

The sectional valve discussed as an exemplary embodiment has a flexibleworking valve seat, and its control valve is configured as an pulsevalve, in such a way that the valve remains open after an actuatingsignal (or pulse), even given an intermittent power failure.

The term “flexible working valve seat” is here to be understood in termsof a movability or displaceability of the working valve seat, and is notgeared toward the working valve seat as such necessarily having toconsist of an elastic material or the like. In the present context, theflexibility of the working valve seat lies in the fact that thesectional valve as a whole, and in particular the working valve seat, isconfigured so that the working valve seat is not rigidly fixed in oneposition, but can rather flexibly and movably follow the working piston.

The “resting state” of the sectional valve here refers to the state inwhich the extinguishing flow is not released, and no actuation signal(e.g., a fire alarm signal during use in a fire extinguishing system) ispresent or was present and still persists. By contrast, the “actuationstate” is the state in which an actuation signal is present or waspresent and still persists, so as to release the extinguishing agentflow, i.e., establish a fluid guiding connection between the inlet(fluid inlet channel) and outlet (fluid outlet channel). In the presentdisclosure, the actuation state does not require that the actuationsignal be continuously applied.

FIG. 1 shows a sectional valve 100 according to the disclosure in aresting state, while FIG. 2 shows a slightly different view of thesectional valve 100 predominantly modified in terms of its manualtrigger in the actuation state.

In the first and second exemplary embodiments, the sectional valve 100according to the disclosure encompasses four assemblies: a working valvewith flexible working valve seat 8, a control valve, a fluid flow signalgenerator as the pressure display or indicator that the sectional valveis open, and a manual trigger.

The working valve comprises a valve body 1, a working piston 2 in apiston chamber 21 of the valve body, an upper valve cover 16, a lowervalve cover 20, an inlet nozzle 18, an outlet nozzle 19, a workingspring 7 designed as a compression spring, a pressure-retaining channelnetwork 22 and a pressure-relieving channel network 23.

The upper and lower valve covers 16, 20 (the designations “lower” and“upper” only serve as a reference to the figures, and are not to beconstrued as a limitation) are secured watertight and gastight to thevalve body 1 by means of screws (not shown).

The inlet nozzle 18 and the outlet nozzle 19 are each screwedinto/flanged to the valve body 1.

The working piston 2 is guided in the piston chamber 21. A seal 40 sealsthe working piston 2 relative to the inner wall of the piston chamber21.

Another seal 3 that interacts with the working valve seat 8 is mountedto the working piston 2 with an attachment bushing 39.

A throttle bore 6 having the smallest cross section of all bores presentin the sectional valve connects the inlet 25 with the piston chamber 21(and above the latter with a pressure-retaining channel network 22). Asieve device 4 is built into the attachment bushing 39, and used toprevent contaminants or the like from the feed line from clogging thethrottle bore 8.

The valve body 1 and upper valve cover 16 are configured so as to have apressure-retaining channel network 22 and a pressure-relieving channelnetwork 23, which are separated in the non-actuated state, andfluidically connected with each other in the actuation state.

Suitable recesses in the upper valve cover 16 and in the working piston2 hold and guide the working spring designed as a compression spring 7,which presses the working piston 2 onto the working valve seat 8.

The control valve comprises a control valve seat 17, a guide bushing 33,an anchor 5, a permanent magnet 29, a control coil 26 around the guidebushing 33, a releasing coil 27 around the permanent magnet 29, a magnetholder 28, a magnetizable core 35 made of magnetizable material, acontrol spring 34, 34′ and an anchor seal 37 in the anchor 5.

FIG. 1 shows a variant in which the control spring 34 abuts against theupper valve cover 16 or a bushing of the control valve in the uppervalve cover 16, while FIG. 2 shows a variant in which the control spring34′ is recessed into the anchor 5, and acts between the anchor 5 andcore 35.

The guide bushing 33 is secured watertight/gastight in the upper valvecover 16, and guides the axial movement of the anchor 5. The core 35 ismounted watertight/gastight in the upper region of the guide bushing 33.The control coil 26 is mounted around the guide bushing 33, and is heldby the magnet holder 28 screwed to the core 35 in a stable positionbetween the magnet holder 28 and upper valve cover 16.

The magnet holder 28 retains the permanent magnet 29 and releasing coil27. The core 35 is in physical contact with the permanent magnet 29, sothat the permanent magnet 29 expands its magnetic field by the length ofthe core 35.

The control valve seat 17 has a bore 36, which is sealed onto the anchor5 and seal 37 by the action of the control spring 34 configured as acompression spring. In the non-actuated state, the seal 37 thusseparates the pressure-retaining channel network 22 from thepressure-relieving channel network 23, so that the second fluidconnection (which here results from the combination ofpressure-retaining channel network 22 and pressure-relieving channelnetwork 23) is closed (i.e., not permeable to fluid).

The fluid flow signal generator encompasses a bushing 11, a signalpiston 13, a seal 14 and a signal spring 15. The signal piston 13 isguided in the bushing 11, and sealed with the seal 14. The bushing 11 ismounted watertight/gastight in the valve body 1. The bushing is joinedwith the outlet 24 on the inlet side. If the outlet 24 is unpressurized(i.e., in the resting state), the signal spring 15 brings the signalpiston 13 into its resting position.

The hand trigger comprises a threaded bushing 30, a threaded bolt 31 anda handle 12. The threaded bushing 30 is built watertight/gastight intothe upper valve cover 16. The threaded bushing 30 is screwed into thethreaded bushing 30, and sealed with the seal 46. The threaded bolt 30is provided with a sealing cone 32, and the handle 12 is provided on thethreaded bolt.

The hand trigger represents an option parallel to the control valve forestablishing a fluid connection between the pressure-retaining channelnetwork 22 and the pressure-relieving channel network 23. With thethreaded bolt 30 completely screwed in, the sealing cone 32 (apart fromthe anchor seal 37) seals the channel network 22 away from the channelnetwork 23.

The exemplary embodiments on FIGS. 1 and 2 differ primarily in how thehand trigger is arranged. As evident on FIG. 2, the hand trigger isthere essentially arranged on the side of the valve 100 opposite theoutlet nozzle 19, while a deviating variant is present in the exemplaryembodiment shown on FIG. 1, in which the handle 12 (the other elementsof the hand trigger are not further denoted or depicted separately onFIG. 1 for the sake of clarity) is arranged on a side of the valve 10adjacent to the outlet nozzle, wherein the details relating to thepressure-relieving channel network 23 correspondingly also differ.However, since the expert is basically familiar with hand triggers ofthis type, there is no need for further explanations. Nonetheless, letit be noted that, because the pressure-relieving channel network 23 isguided differently, its connection to the piston chamber 21 is not shownon FIG. 1 (i.e., is present outside of the drawing plane).

The subassembly of the flexible valve seat comprises the working valveseat 8, a seal 9 and a working valve spring 10.

The subassembly 8 is guided in the valve body 1. The seal 9 providedbetween the working valve seat 8 and a wall of the valve body 1 sealsthis guide for the working valve seat 8. In the non-actuated state, theworking valve seat 8 with the seal 3 seals the inlet 25 from the outlet24, and separates the latter from each other. The working valve seat 8has a range of movement between a complete compression of the workingvalve spring 10 and an abutment in the valve body 1. The flexibility ofthe working valve spring 10 makes it possible to lift the working valveseat 8 from the working piston 2 by a certain distance, or the workingvalve seat 8 can follow the working piston 2 until it comes to abut.

In the exemplary embodiments shown on FIGS. 1 and 2, the respectiveworking valve is provided with the working valve spring 10, whichapplies the valve seat force that presses the working valve seat 8 ontothe working piston 2 or prevents the working valve seat 8 fromdeflecting while pressing the working piston 2 into the working valveseat 8. Alternatively, it is also possible to produce the valve seatforce in the operating state using an area difference between opposingend faces of a working valve seat (not depicted in this way here), whichis guided in the valve body. In the operating state, a pressure ispresent in the inlet 25. If the end faces that are perpendicular to thelongitudinal direction in which the working valve seat is guided, whichare each exposed to the pressure prevailing in the inlet, vary in size,this yields a resultant differential force that can be used as the valveseat force. The size of the end face exposed to the pressure is to beunderstood as the size of a projected area produced by projecting thesurfaces exposed to the pressure onto a plane perpendicular to therespective direction.

If the valve seat force is produced solely based on the area differenceof the pressurized end faces, the working valve seat is preferablyguided in the valve body in such a way that two abutments are present, afirst abutment (as also discernible on FIGS. 1 and 2) that limits theextent to which the working valve seat runs after the working piston(since the sectional valve could otherwise not be opened), and a secondabutment that lies opposite the first abutment, with which the guidepath of the working valve seat in the valve body in the oppositedirection is limited, so that the working valve seat is held in thevalve body secured against loss. Under certain conditions, however, thesecond abutment can be omitted if concern over the working valve seatbeing lost were to be eliminated, for example because of other measures.

In each hydraulic system, undesired hydraulic shocks can arise forvarious reasons. These shocks can result in mechanical components of thesystem becoming loaded to such an extent that the latter malfunction.One example for a malfunction of a conventional sectional valve is whenthe piston is briefly lifted due to a shock, causing the sectional valveto open.

The job of the flexible working valve seat 8 is to compensate for thelifting of the working piston 2 as the result of shocks, and thus keepthe sectional valve 100 closed to a desired degree of lift.

This is achieved by having the working valve seat 8 lag the workingpiston 2 by the desired degree through exposure to the force of theworking spring 10, and further exert a compressive force on the seal 3,so that the sectional valve remains closed, and no fluid conductingconnection exists between the inlet 25 and outlet 24.

As already discussed above, the advantage to the movable working valveseat 8 is that pressure fluctuations in the inlet 25 eliminate orgreatly diminish the chance of the sectional valve 10 becomingpermeable, since the working valve seat 8 follows the working piston 2even given a pressure spike, and thereby maintains a closed state of thesectional valve 100.

When using the sectional valve in a water extinguishing system (anextinguishing system with water or water-based extinguishing agent asthe fluid), the pipe network (not shown) is divided into protectiveregions, wherein each region is separated by at least one valve (thenalso referred to as a selector valve). The extinguishing agent isusually guided from a supply location through a distribution line withsuch valves in various fire protection sections. When a pump dispatchesfluid with a pressure p₂ plus a pressure spike in order to maintain thepressure p₁ applied (and desired) at the inlet in the resting state, itmay happen in conventional sectional or selector valves that one or morenon-actuated valves open. In the context of the present disclosure, thisopening (at least for a pressure spike Δ₁) is prevented by the movableworking valve seat 8, even if the pressure surges constitute a multipleof the normal operating pressure.

For example, the pressure p₁ in the resting state can measure 140 bar,and is maintained by a resting pressure pump (regulation at approx. 2bar).

In the resting state, the sectional valve 100 is closed. Pressure p₁prevails in the inlet 25. Due to the fluid connection between the inlet25 and piston chamber 21 provided by the throttle bore 6, the pressurep₁ thus also prevails in the piston chamber 21. As a result of thelarger first active pressure surface of the working piston 2 arranged inthe piston chamber 21, the working piston 2 is held in the restingposition by the resultant force on the first active pressure surface,which is greater than the force on the second active pressure surface ofthe working piston 2 in the inlet 25. In this resting position, there isno fluid conducting connection between the inlet 25 and outlet 24.

In order for the sectional valve 100 to open, i.e., a fluid conductingconnection to be established between the inlet 25 and outlet 24, theworking piston 2 is lifted from its working valve seat 8. To this end, apressure drop is created in the piston chamber 21, specifically byopening a second fluid connection via the control valve, which actsbetween the pressure-retaining channel network 22 (which is continuouslyconnected with the piston chamber 21) and the pressure-relieving channelnetwork 23 (which is continuously connected with the outlet 24, but canalso lead to a separate reservoir independent of the outlet 24). To openthe control valve, the anchor 5 is lifted from the control valve seat17, thereby establishing a fluid connection between the channel networks22 and 23.

According to the disclosure, the permanent magnet 29 is removable(preferably also replaceable). The control valve (in the form of asolenoid valve) is designed in such a way that it can be equipped withan anchor holding device (AH) or “anchor holding and control device”(AHS) according to a modular principle, wherein a conversion between AHand AHS is preferably possible.

The difference between AH and AHS lies in the fact that, by comparisonto the simpler anchor holding device (not shown), the anchor holding andcontrol device is equipped with an additional coil (releasing coil 27)to suppress the effect of the permanent magnet 29.

In a conventional solenoid valve (not shown) without an anchor holdingdevice, the valve is only open when a strong enough current is flowingat the control coil, since the control spring presses the anchor ontothe control valve seat in the absence of current flow. Therefore, aconventional solenoid valve without an anchor holding device is closedgiven a power failure or deactivated power. By contrast, the desire infire protection technology is that the actuated sectional valves alsostill remain actuated after an extinguishing process has beenintroduced, even if energy supply can no longer be guaranteed owing tofire damage, so that the extinguishing process can continue to beensured.

If the anchor holding device (i.e., here the permanent magnet 29 in themagnet holder 28) is provided, the anchor 5 remains adhered to thepermanent magnet 29 (more precisely indirectly via the core 35) duringthe opening process (actuation state), so long as the current signal 26provides for a sufficient lifting of the anchor 5 from the control valveseat 17 (or a sufficient approach by the anchor 5 to the core 35), i.e.,the control valve remains open even given a power failure. During amechanical (manual) removal of the permanent magnet 29 (for example,after extinguishing is complete), the control valve returns to theclosed setting. The permanent magnet 29 here thus has the function of ananchor holding device (AH).

Beyond the configuration of an anchor holding device, the exemplaryembodiments shown on FIGS. 1 and 2 also encompass the function of ananchor holding and control device.

As already the case with the anchor holding device, the anchor 5 in thisversion also adheres to the permanent magnet 29 (or the core 35magnetized by the permanent magnet 29) initially after opening thevalve, wherein manually removing the permanent magnet 29 also leads to aclosing of the control valve. In addition, a current flow through thereleasing coil 27 (switching signal “Valve closed”) can generate acompensating magnetic field, which releases the anchor 5. (bi-stablesolenoid valve). However, this valve remains in an open setting given apower failure here as well.

Another embodiment of the disclosure can also provide that thecircumstances of the open setting and closed setting of the controlvalve be switched, so that this type of valve would be in the opensetting in a resting state, and would be kept there by the magnet in aclosed setting.

In the exemplary embodiments illustrated on FIGS. 1 and 2, the core 35is screwed into the guide bushing 33, meaning that the core 35 can be(variably) positioned in any screw-in depth desired.

A tightness of the core 35 relative to the guide bushing 33 is hereensured by an O-ring seal (not shown), which is entrained in the core35, regardless of the setting (screw-in depth) at which the core 35 ispositioned in the guide bushing 33.

This property (core 35 has a variable screw-in depth) makes the lift ofthe anchor 5 variable as well. Since the magnetic force of the controlcoil 26 acts analogously to the position of the anchor 5, this meansthat the desired force of attraction can also be variably selected forthe control coil by determining the anchor lift. This indirectlyinfluences a determination of the bore size of the control valve seat17, which the anchor 5 acts upon and seals via the hydraulic pressure,and the determination of the flow as a function of lift.

The sectional valve in the first and second exemplary embodimentsencompasses a fluid flow signal generator. The assembly of the fluidflow signal generator (bushing 11, signal piston 13, seal 14, signalspring 15) has the function of signaling the fluid flow or pressureapplication upon release of the fluid conducting connection from theinlet 25 to the outlet 24. In a resting state, the signal piston 13 isin a resting position. In the actuation state (fluid flows), thepressure of the fluid on the end face of the signal piston 13 (oppositethe force exerted by the signal spring 15) pushes the signal piston 13into a signaling position.

One advantage to this mechanical fluid flow signal generator (thatresponds to a pushing or thrusting motion) lies in the ability to testthe functionality from outside, without emptying the fluid-carryingcomponents, by manually “pressing” (or pulling) the signal piston 13(spring locked, spring defective due to breakage/corrosion).

In the non-actuated state schematically shown on FIG. 1, the operatingpressure, e.g., 140 bar, acts in the inlet 25, in the throttle bore 6,in the piston chamber 21 and in the pressure-retaining channel network22.

The outlet 24 is unpressurized when conventionally connected withpressure-relieving open nozzle pipe networks. In these exemplaryembodiments, the pressure-relieving channel network 23 is connected withthe outlet 24, thus making it unpressurized as well.

The working piston 2 presses the working valve seat 8 against theworking valve spring by a lift, and seals the inlet 25 and outlet 24from each other with the seal 3.

The active force exerted by the pressure in the pressure-retainingchannel network 22 and the control spring 34 designed as a compressionspring on the core 5 or anchor seal 37 seals the bore 36 of the controlvalve seat 17, so that the pressure-carrying channel network 22 and thepressure-relieving channel network 23 are separated from each other.

The signal piston 13 of the fluid flow signal generator is in itsunpressurized resting position.

The sealing cone 32 seals or separates the pressure-retaining channelnetwork 22 and the pressure-relieving channel network 23 from each otherat a second location.

During fire detection in a fire section, for example, the control coil26 is actuated via a control center (not shown) (for example, firedetector and/or extinguishing control center). The control coil 26 thengenerates a magnetic field, which moves the anchor 5 against the controlspring 34 to abut against the core 35. The anchor 5 remains adhered tothe core 35, even if power to the coil 26 was turned off.

Releasing the bore 36 causes the pressure to quickly dissipate from thepiston chamber 21 via the then existing fluid connection comprised ofthe channel networks 22 and 23 to the unpressurized outlet 24, since thethrottle bore is unable to allow the influx of extinguishing agentarriving through the fluid connection.

A resultant force in this way arises in the working piston, which allowsthe working piston 2 (and the working valve seat 8 that initiallyfollows the piston) to move in the flow direction, until the workingpiston 2 finally exits the working valve seat 8 after the joint lifting,and eliminates the separation of fluid chambers 24 and 25. As aconsequence, the sectional valve 100 is opened.

The signal piston 13 of the fluid flow signal generator is exposed topressure, and pushed to abut against the bushing 11 against the springforce of the signal spring 15.

The power supply to the control coil 26 is turned off at the conclusionof the extinguishing process at the latest, which eliminates themagnetic field of the control coil 26.

At least one brief current pulse on the releasing coil 27 builds up acounteracting magnetic field around the permanent magnet 29, whicheliminates or at least limits the retaining force of the permanentmagnet 29 and core 35. The anchor 5 is thereby released, and the effectof the compression and spring force exerted by the control spring 34causes the anchor 5 to close the bore 36.

The operating pressure in the piston chamber 21 is built up againthrough the throttle bore 6, the working piston 2 again moves toward theworking valve seat 8, and presses the valve seat 8 one lift incrementlower.

The sectional valve 100 is thus closed again.

The spring force exerted by the signal spring 15 returns the signalpiston 13 to its resting position.

If necessary, the sectional valve 100 is manually actuated (heremanually opened). Turning the handle 12 or threaded bolt 31 causes thesealing cone 32 to open the pressure-retaining channel network 22 to thepressure-relieving pressure channel network 23, and the valve opens asdescribed above. Turning the handle in the opposite direction causes thesealing cone 32 to seal the pressure-retaining channel network 22 again,and the valve closes as described above.

Instead of the closing process described above involving the use of thereleasing coil 37, the permanent magnet 29 itself can be removed farenough away from the core 35 that the force of the control spring 34,34′ predominates, and again moves the anchor 5 into the closed position.

It is likewise possible to use the control coil itself to generate thedesired releasing magnetic field to offset/reduce the effect of thepermanent magnet. This can be achieved by reversing the direction ofcurrent through the control coil by means of a suitable switch.

FIG. 3 shows an exemplary embodiment of a method according to thedisclosure for controlling a sectional valve for an extinguishing agentline.

Just as in the exemplary embodiments described above, for example, thesectional valve discussed here has a control valve and a working valve,which is configured for a pilot control by the control valve. Theworking valve comprises a throttle bore, which establishes a first fluidconnection between a pressure-retaining inlet of the sectional valve anda piston chamber of the working valve, and a working piston, wherein afirst end face of the working piston is larger in relation to the pistonchamber than a second end face in relation to the inlet. The controlvalve further comprises a control valve seat, an anchor which, whenpressed onto the control valve seat, together with the control valveseat closes a second fluid connection between the piston chamber and anoutlet of the sectional valve, a magnetizable core and a control coil,which is configured to exert a magnetic force on the anchor.

The second fluid connection is opened and closed with the control valve,wherein the anchor is lifted from the control valve seat in the openingprocess to the point where the second fluid connection allows a greaterflow than the first fluid connection.

In step 50, the sectional valve is provided, while in step 51, a forceto be applied by the control coil to achieve the actuation state is setby variably positioning the core along a force produced by the controlspring. This step 51 can be followed by (potentially permanently) fixingthe position, for example by bonding or welding.

In step 52, the sectional valve is moved into the resting state. In thisstate, the control spring presses the anchor onto the control valveseat, so that the second fluid connection is closed.

In step 53, the control coil is supplied with current, so that the thenacting magnetic force lifts the anchor from the control valve seatagainst the effect of the control spring, thereby opening the controlvalve.

In step 54, the control coil moves the anchor close enough to the corethat the force exerted on the anchor by the permanent magnet via thecore is large enough to hold the anchor in the lifted state against thecontrol spring.

Parallel thereto in step 55, opening the second fluid connection leadsto a drop in pressure in the piston chamber, so that the differentialpressure between the piston chamber and inlet causes a force to act onthe working piston that ultimately ensures the opening of the sectionalvalve, i.e., the opening of a connection between the inlet and outlet.

In step 56, the permanent magnet is removed from the sectional valve, sothat the force countering the control spring is eliminated or at leastsufficiently diminished, so that the control spring presses the anchoronto the control valve seat, thereby closing the second fluidconnection.

Since extinguishing agent continues to flow through the throttle boreinto the piston chamber, but no longer flows out through the secondfluid connection, the pressure in the piston chamber (again) arises fromthe inlet in step 57, so that the varying end faces of the workingpiston now yield a resultant force that together with the working springpresses the working piston onto the working valve seat, thereby closingthe sectional valve.

The resting state is thus reached once again, so that the process can beresumed at the appropriate time starting at step 52, for example, oncethe permanent magnet has been reset.

In an alternative or supplemental configuration, the anchor can bepressed onto the control valve seat by means of the core via thepermanent magnet prior to the actuation state, wherein the control coilis configured to lift the anchor from the control valve seat against aretaining effect of the permanent magnet, wherein the permanent magnetis held in and/or on the magnet holder, and the permanent magnet isremoved for a transition into the actuation state, wherein the anchorlifted from the control valve seat is held by a control spring in theactuation state.

REFERENCE LIST

-   1 Valve body-   2 Working piston-   3 Seal-   4 Sieve device-   5 Anchor-   6 Throttle bore-   7 Working spring (Compression spring)-   8 Working valve seat (Valve seat)-   9 Seal-   10 Working valve spring (Spring)-   11 Bushing-   12 Handle-   13 Signal piston (Piston)-   14 Seal (Sealing ring)-   15 Signal spring (Compression spring)-   16 Upper valve cover-   17 Control valve seat (Seat)-   18 Inlet nozzle-   19 Outlet nozzle-   20 Lower valve cover-   21 Piston chamber-   22, 23 Second fluid connection (Combination of pressure-retaining    channel network+pressure-relieving channel network)-   24 Outlet (Fluid outlet channel)-   25 Inlet (Fluid inlet channel)-   26 Control coil (First coil)-   27 Releasing coil (Second coil)-   28 Magnet holder-   29 Permanent magnet-   30 Threaded bushing-   31 Threaded bolt-   33 Guide bushing-   34 Control spring (Compression spring)-   35 Magnetizable core-   36 Bore of control valve seat-   37 Anchor seal-   39 Attachment bushing-   40 Seal-   100 Sectional valve

1. The valve (100) according to claim 12, comprising: a control valveand a working valve, which is designed for pilot control by the controlvalve, with: a throttle bore (6) that establishes a first fluidconnection between the inlet (25) of the valve (100) to be pressurizedand a piston chamber (21) of the working valve, and a working piston (2)with a first end face opposite the piston chamber that is larger than asecond end face opposite the inlet (25), wherein the control valve isconfigured to open and close a second fluid connection (22, 23) betweenthe piston chamber (21) and the outlet (24) of the valve (100), whereinthe control valve further has: a control valve seat (17), an anchor (5)that closes the second fluid connection (22, 23) together with thecontrol valve seat (17) when pressed onto the control valve seat (17), amagnetizable core (35) and a control coil (26) configured to exert amagnetic force on the anchor (5), such that the control coil (26) liftsthe anchor (5) from the control valve seat (17) to an extent that thesecond fluid connection (22, 23) allows a greater flow than the firstfluid connection, characterized in that the control valve has a)—acontrol spring (34, 34′), which presses the anchor (5) onto the controlvalve seat (17), and against which the control coil (26) lifts theanchor from the control valve seat (17), a permanent magnet (29), whichin an actuation state is configured to hold the anchor (5) lifted fromthe control valve seat (17) indirectly by the core (35), and a magnetholder (28), in and/or on which the permanent magnet (29) is held in theactuation state, and which allows a removal of the permanent magnet(29), or b)—a permanent magnet, which presses the anchor (5) onto thecontrol valve seat (17) indirectly by the core (35), and against theretaining effect of which the control coil (26) lifts the anchor (5)from the control valve seat (17), a control spring, which in anactuation state is configured to hold the anchor (5) lifted off of thecontrol valve seat (17), and a magnet holder (28), in and/or on whichthe permanent magnet is held, and which allows a removal of thepermanent magnet for a transition into the actuation state, and/orcharacterized in that the control valve is configured to variablyposition the core (35) along the longitudinal axis by the forcegenerated by the control spring (34, 34′). 2.-11. (canceled)
 12. A valve(100) for switching fluids with an inlet (25) and an outlet (24),wherein a fluid conducting connection between the inlet (25) and outlet(24) is closed with the valve (100) in a resting state, wherein thevalve (100) has a fluid flow signal generator with a bushing (11) and asignal piston (13) guided in the bushing (11) with an outlet end face,to which the pressure prevailing in the outlet (24) of the valve isapplied, wherein the signal piston (13) is held in a resting position bya signal spring (15) in an unpressurized state, and the signal piston(13) extends outwardly through the bushing (11), so that a position ofthe signal piston (13) is discernible from outside, and/or the valve(100) has a detection means for detecting a predetermined deviation ofthe signal piston (13) from the resting position.
 13. The valve (100)according to claim 12, wherein detection takes place by a closing and/oropening of a mechanical, electrical, magnetic and/or optical contactgiven at least the predetermined deviation of the signal piston (13)from the resting position.
 14. The valve (100) according to claim 12,wherein the signal piston (13) has a seal (14) relative to the bushing(11), which is located between the outlet (25) and signal spring (15)and/or in an outer wall of the bushing (11).
 15. The valve (100)according to claim 12, wherein the signal piston (13), in particulargiven an unpressurized outlet (24), can be moved through exposure to anoutside force in the direction of the outlet (24) and/or opposite thisdirection to check the function.
 16. The valve (100) according to claim12, wherein signal piston (13) and signal spring (15) are dimensioned insuch a way that the signal piston (13) comes to abut against the bushing(11) given a predetermined pressure in the outlet (24).
 17. Anextinguishing system with an extinguishing agent line and a valve (100)according to claim
 12. 18. (canceled)